Fluid power apparatus



May 17, 1966 A. L. GOOD FLUID POWER APPARATUS 4 Sheets-Sheet 1 FiledOct. 2, 1964 IN V EN TOR.

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May 17, 1966 A. GOOD FLUID POWER APPARATUS 4 Sheets-Sheet 2 Filed Oct.2, 1964 INVENTOR. fl/Ff/vl/P Z 6000 M 3 g n May 17, 1966 oon FLUID POWERAPPARATUS 4 Sheets-Sheet 5 llln INVENTOR. fikr/we L 6000 77 BY v FiledOct. 2, 1964 May 17, 1966 A. L. GOOD FLUID POWER APPARATUS Filed Oct. 2,1964 4 Sheets-Sheet 4 M -vmwk 5 7 /3 a a I no ma 33 I38 434 a jig 13 3377 ll ll 66 W fi v IN V EN TOR. HRTHUR 4, 600a United States Patent3,251,443 FLUID POWER APPARATUS Arthur L. Good, 1549 Cone St., Eikhart,Ind. Fiied Oct. 2, 1964, Ser. No. 401,074 13 Ciairus. (Cl. 192 -61) usedwidely by means of which a fluid is forced through a circuitous path toaccomplish one of many effects. Such effects include the operation ofmachinery, the transport of fluids from one place to another, andthe'like. In such cases power is applied in a suitable way to theapparatus. On the other hand it is frequently the practice to provideapparatus through which a fluid under pressure is forced and from whichpower can be taken ofl.

Devicesof the kinds referred to have heretofore consisted of certainconventional assemblages of parts. One such assemblage is the well knowngear pump in which a pair of meshing gears, each rotating in a closelyfitting chamber, can be employed, when power driven, to forward a fluidthrough the pump to an external circuitous path to accomplish a desiredeffect or to pump the fluid from one location to another. By omittingthe power source to drive the gears and by forcing fluid through the ap-I paratus under pressure the gears are rotated and power can be takenoff from the apparatus by a suitable means.

Another common device is the well known vane pump in which a cylindricalmember rotates nonconcentrically in a cylindrical chamber of largerdiameter than the member and in which the circular member is providedwith a vane reciprocating in an essentially radial slot in the member,the outer end of the vane being adapted to wipe the inner surface of thecylindrical chamber. By suitably locating the parts and by providingsuitable ports through which the fluid can enter and leave the part ofthe chamber not occupied by the cylindrical member, the apparatus can beused to pump fluid under considerable pressure either to transfer thefluid or to operate a suitable machine. -On the other hand, when a fluidis forced through a suitable modification of the apparatus, power can betaken ofi from it. In some instances the member and chamber are notentirely cylindrical.

In the foregoing and other equivalent devices a fluid is displaced bythe apparatus when the apparatus is power driven and the fluid isforwarded to a desired location. Such devices are sometimes referred toas fluid displacement devices. In apparatus of the foregoing andequivalent kinds through which fluid is forced under pressure, e.g. froman outside source, and from which power is taken off, the fluidcirculating through the apparatus some instances used to a considerableextent, they each" have disadvantages and are often unreliable,inefficient, and in certain instances not adapted to high speed use.

-Furthermore, they are invariably costly to manufact-ue and generallyrequire frequent and extensive servicing. In addition, such devices arenot generally well adapted 3,251,443 Patented May 17, 1966 to use asvariable speed power transmitting devices which in many operations isessential.

The present invention is concerned with apparatus which can, by suitablemodification, function in some instances as a fluid displacement device,in some instances as a fluid motor, in some instances either as a fluiddisplacement device or asa fluid motor and in still other instancesessentially as both a fluid displacement device and'a fluid motor at'thesame time with power being applied to one part of the appartus and powerbeing taken off from another part of the apparatus.

For want of a better term, the term fluid power apparatus is used'hereinto include apparatus through which a fluid circulates and suitablemodifications of which are adapted to use as (l) a fluid displacementdevice, (2) a fluid motor, (3) either a fluid displacement device or afluid motor, and (4) a variable speed power transmitting device whereinone part of the apparatus is power driven and power is taken off fromanother part of the same apparatus. In the latter instance the path ofthe circulating fluid can lie wholly within the fluid power apparatus orpartially within and partially outside theapparatus.

It is, therefore, an object of the present invention to provide a fluidpower apparatus by means of which fluid can be circulated to accomplisha desired effect.

An additional object is to provide a fluid power apparatus useful forforwarding a fluid under pressure to deliver power to a desired machineor location.

An additional object is to'provide a fluid power apparatus free of gearsand reciprocating vanes which function as fluid-forwarding elements.

An additional object is to provide a fluid power apparatus useful as afluid displacement device.

An additional object is to provide a fluid power apparatus useful as afluid motor.

An additional object is to provide a fluid power apparatus useful eitheras a fluid displacement device or as a fluid motor.

An additional object is to provide a fl-uid power apparatus useful as apower transmitting device.

An additional object is -to provide a fluid appartus useful as avariable speed power transmitting device which is highly eflicient inthe transmission of power and which is adjustable to a predeterminedspeed of the power take off. I

An additional object is to provide a fluid power apparatus useful as avariable speed power transmitting device which is economical tomanufacture and which is rugged in operation and requires infrequentservicing.

An additional object is to provide a fluid power apparatus useful as avariable speed power transmitting device adapted to apply a low startingtorque for heavy loads and to maintain an essentially constant speedonce the desired speed has been attained.

An additional object is to provide a fluid power apparatus useful as avariable speed power transmitting devicewhich can be installed in placeof a conventional pulley or gear on the end of a driven shaft.

Other advantages of the invention will be apparent as the descriptionproceeds.

Although the term fluid includes both liquids and gases, it is often thecase that apparatus of this invention is concerned with liquids ratherthan with gases and to this extent, the apparatus is a hydraulicapparatus; However, it will be apparent from the description that inmost instances the apparatus of this invention can be used with gases aswell as with liquids, even though the employment of hydraulic liquidsmay be preferred. Although the apparatus will, therefore, be describedwith particular reference to its use with liquids, especially in thedescription is taken off from the-other assemblage.

of its use as a variable speed power transmitting device, it is to beunderstood that the invention encompasses also the operation of theapparatus with gases in instances where such use is advantageous orappropriate.

Generally, speaking, the fluid power apparatus of this inventioncomprises first and second assemblages of members which cooperate withone another in the way which will be described. Generally speaking,also, it will be apparent that when the apparatus is power driven, powercan often be applied to either the first or the second assemblage, asdesired, and that the apparatus is reversible so that fluid can becaused to flow through it in either direction.

Since one important application of the apparatus is as a variable speedpower transmitting device, the invention will be described first, andwith particular emphasis, with respect to its employment for thatpurpose. In such instance one of the assemblages is power driven andpower For the sake of clarity in describing this modification of theinvention, the assemblage to which a power input source can be connectedwill be assumed to be the first assemblage and, since it serves to drivethe second assemblage, the first assemblage will, for the sake offurther clarity, frequently be referred to as the driving assemblage. Insimilar manner the second assemblage, which is driven by the drivingassemblage and from which power can be taken off will frequently bereferred to as the driven assemblage.

In any modification the first and second assemblages ro tate coaxiallywith one another and cooperating with one another in the way which willbe described.

Briefly, the first assemblage includes one or more rotor vane cavities,or chambers, in each of which a suitable vane provided with a pluralityof rotor vane tips, usually referred to as a rotor vane, rotates,generally with a tip in essentially fluid-tight relationship with thewall thereof. The second assemblage includes a fluid-forwarding chamher, one surface of which is wiped by a rotor vane tip, generally inessentially fluid-tight relationship with the wall thereof, the rotorvane chamber and the fluid-forwarding chamber being alternately incommunication with and noncommunicating with one another. Suitable firstand second fluid-conveying duct systems located in the second assemblageserve to convey fluid, by way of corresponding first and second ports,into and out of, respectively, the fluid-forwarding chamber. When theapparatus is to be employed for forcibly forwarding a fluid, one of theassemblages, e.g. the first assemblage, is power driven. When theapparatusis to be employed as a fluid motor, fluid is circulatedforciblythrough the fluid-forwarding chamber to effect rotation of at least oneof the assemblages.

In the event the fluid is to be delivered by the apparatus to a suitablereceiver or machine located externally of the apparatus, one ductsystem, i.e. the second duct system in the second assemblage, isconnected with a suitable conduit for delivering the fluid to thedesired location and another appropriate fluid-conveying duct system,i.e. the first duct system in the second assemblage, is connected with asuitable conduit for conveying a supply of fluid to the apparatus. Inthe event the apparatus is utilized to forward fluid under pressure tooperate another device or machine, it generally follows that the exhaustfluid from the operated device or machine can be conveyed back to thefluid power apparatus and recirculated.

When the fluid power apparatus is used to deliver fluid to a locationexternal to the apparatus, one of the assemblages is usually mountedrigidly and prevented from rotating to facilitate the connection ofsuitable conduits to it, power being in this instance applied to theother assemblages. When, however, a suitable modification of the fluidpower apparatus is utilized as a variable speed power transmittingdevice, it is convenient to connect the first and second duct systemstogether within the second assemblage to provide a continuous closedpath for flow of fluid out of and into the fluid-forwarding chambers.Power can then be applied to rotate one of the assemblages and power canbe taken off from the other assemblage. By installing a suitable fluidflow-restricting means in the path of the flow of fluid within thesecond assemblage, rotation of both the first and second assemblages canbe effected by driving one of the assemblages, e.g. the firstassemblage, the relative rotational speed of the second, or driven,assemblage with respect to that of the first or driving assemblagedepending upon the degree of restriction of fluid flow by theflow-restricting means. By making the degree of fluid restrictionresponsive to the actual speed of rotation of the driven assemblage,power can be taken off from the driven assemblage at an essentiallyconstant rotational speed. These matters will be clear as thedescription proceeds.

The invention can be understood readily by reference to the accompanyingdrawing wherein, in the interest of clarity, certain features are shownon'a somewhat exaggerated scale and wherein:

FIGURE 1 is an elevation, somewhat schematic, of a variable speed powertransmitting device embodying features of the invention;

FIGURE 2 is an end elevation taken along the line IIII of FIGURE 1;

FIGURE 3 is an elevation, principally in section, of the device ofFIGURES 1 and 2 taken along the broken line IIIIII of FIGURE 2 and,correspondingly, along the broken line IIIIII of FIGURE 4;

FIGURE 4 is a sectional elevation taken along the line IVIV of FIGURE 3showing the relative positions of certain of the parts at one stage inthe operation of the device;

FIGURE 5 is a sectional elevation corresponding to FIGURE 4, but showingthe relative positions of certain of the parts at a different stage inthe operation of the device;

FIGURE 6 is a sectional elevation taken along the line VIVI of FIGURE 3showing the relationships of certain of the parts with respect to oneanother;

FIGURE 7 is a sectional elevation taken along the line VIIVII of FIGURE3 showing the relationships of certain others of the parts with respectto one another;

FIGURE 8 is a view, principally in section, illustrating certainfeatures of one modification of the apparatus of the invention useful asa reversible pump for fluids;

FIGURE 9 is a schematic sectional illustration showing certain featuresof yet another modification of the apparatus of the invention;

FIGURE 10 is a schematic sectional illustration showing certain featuresof still another modification of the apparatus of the invention;

FIGURE 11 is a diagrammatic illustration showing certain features of amodification of the apparatus of the invention employing a camarrangement in place of gears;

FIGURE 12 is a schematic sectional illustration showing certain featuresof another modification of the apparatus of the invention.

FIGURE 13 is a schematic sectional illustration corresponding to FIGURE12, but showing different positions of certain of the parts; and

FIGURE 14 is a diagrammatic illustration of a modi fication of theapparatus of the invention useful for producing a pulsed flow of fluid.

As indicated previously the apparatus of the invention will be describedfirst, and in greatest detail, with reference to a modification adaptedparticularly to use as a variable speed power transmitting device asillustrated in FIGURES 1-7, inclusive. A hydraulic liquid is preferablyemployed as the circulating fluid in this instance.

Referring to FIGURES 1 and 3, the variable speed power transmittingdevice illustrated includes a shaft coupling 42 of appropriate internaldiameter to accommodate the end of a driven power shaft (not shown) andwith suitable means, such as key lock screws 45, to secure the couplingin conventional fashion on the end of the shaft. The shaft coupling 42,is suitably contoured externally along an intermediate section 61 of itslength inwardly of the apparatus to provide a seat for a main or outerbearing, suitably a seat for the inner race 48 of a roller bearing 49.The disposition of the outer race 50 of the bearing 49 will be referredto later. The coupling 42 is prolonged inwardly of the intermediatesection 61 and is suitably of reduced outer diameter along its inner endsection 62. The inner end section 62 is bored axially and threadedinternally to accommodate an externally threaded rotor adjusting screw41 which is locked at its outer end, as by a lock nut 40. The bore ofthe inner end section 62 of the coupling 42 is conveniently of lesserdiameter than the bore of the outer and intermediate end sections of thecoupling. The configuration and function of the inner end of the rotoradjusting screw will be mentioned later. I

The rotor adjusting screw 41 is bored axially and threaded internally toaccommodate a bearing adjusting screw 38 and a lock screw 39 therefor.An unthreaded and suitably somewhat larger inner section 63 of the innerend of the bore of the rotor adjusting screw 41 accommodates theprotruding center shaft 64 of a suitably dish-shaped bearing adjustingplate 32. The rim 65 of the bearing adjusting plate 32 bears on theouter race 31 of an inner bearing 30, the disposition and functioning ofwhich will be referred to later. The outer end of the bearing adjustingplate shaft 64 bears against the inner end of the bearing adjustingscrew 38 by means of which the location of the plate 32 can be adjusted.Suitable seals, such as a rotor adjustment seal 1 and a bearingadjustment seal 3, are conveniently provided to prevent passage ofhydraulic fluid outwardly of the apparatus around the rotor adjustingscrew 41 and around the bearing adjusting plate shaft 64, respectively.

A rotor 33 is provided which is of generally cylindrical exteriorconfiguration with planar end faces and is bored axially and secured, asby keys 36 and suitable keyways, to the outer surface of the inner endsection 62 of the coupling 42 so as to rotate therewith. A rotor frame5, also of generally cylindrical exterior configuration with a diametersomewhat greater than that of the rotor, is mounted with its planarouter end face in flat face to face nonrotational contact with the innerend face of the rotor 33. The rotor frame is bored axially, a shortlength of the bore adjacent to the rotor having a diameter approximatelythe same as or somewhat larger than, that of the bore of the inner endsection 62 of the coupling 42. The inner end of the short length of therotor bore is enlarged, e.g. flared outwardly, to accommodate thecorrespondingly enlarged and contoured inner end, or head, 103 of therotor adjusting screw 41. By turning down the screw 41 and tighteningthe lock nut 40 the rotor frame is secured against the inner end of therotor 33, although additional securing means is provided as will bementioned later.

As is shown in FIGURES 4 and 5, and as will be explained in detaillater, the rotor 33 in the modification illustrated is provided withfour vane cavities or chamhere 7 spaced equally around its periphery. Arotor vane 2 is located rotatably in each vane chamber. Each vane unitcomprises a rotor vane shaft 72 extending axially from one side of thevane through an appropriately located bore and rotor vane bearing 6 inthe rotor frame 5. The outer end of the rotor vane shaft 72 is threadedto receive a rotor vane nut 8. A rotor vane gear 7 is secured, as by arotor gear key 54, to the shaft between the nut 8 and the adjacent faceof the rotor frame 5.

The rotor 33 and the rotor frame are also provided with registeringholes to receive a pair of oppositely located idler gear bolts 35, theholes in the rotor being threaded internally and being located betweenthe vane chambers 70. The bolts 35 are each provided near their headswith a section of enlarged diameter providing a shoulder to bear againstthe rotor frame when the bolts are tightened down to assist in securingthe rotor 33 and the rotor frame 5 securely together. The enlargedsection of each bolt also provides for the mounting, by way of asuitable bearing 27, of an idler gear which runs freely on the bolt. Apair of securing bolts 57, shown particularly in FIGURE 6, are provided,usually on the same radius as, and spaced equallybetween the pair ofidler gear bolts 35, to further assist in securing the rotor 33 and therotor frame 5 together. The axial bore of the rotor frame 5, except forthe short length facing the shaft coupling 42 referred to, issufiiciently large to enclose the bearing adjusting plate 32 and toprovide a seat for the outer race 31 of the inner bearing 30.

It will be seen from the foregoing that the assemblage of the elementscomprising the shaft coupling 42, the inner race 48 of the bearing 49,the rotor 33, the rotor vanes 2, the rotor frame 5, the bearingadjusting plate 32, the outer race 31 of the bearing 30 and associatedparts rotates as a unitary assemblage. As indicated previously, thisunitary assemblage can be referred to conveniently as the drivingassemblage of the apparatus.

The driven assemblage will now be described.

A rotor housing 4 of suitable dimensions is provided which is ofgenerally cylindrical configuration. The rotor housing can be providedwith external fins for cooling if desired. The inner contour of therotor housing will be described later. The end face of the rotor housingnearest the main bearing 49 is recessed to receive a circular wear plate37 and the adjacent part of a main bearing housing 53, a suitablebearing housing seal 34 being inserted between the projecting rim of therotor housing 4 and the inset part of the main bearing housing 53 toprevent the passage of hydraulic fluid outwardly between them. The mainbearing housing 53 is provided with a circumferential flange 104, whichbears against the extreme end of the rotor housing 4 to position theseelements accurately with respect to. one another.

The circumferential inner face of the main bearing housing 53 is planarand is adapted to bear on wear plate 37 in flat face to facerelationship. The parts are dimensioned to cause the plane of thecircumferential inner face of the housing 53, but when the housing isproperly seated, to clear by a suitable distance all but the inner endsection 62 of the shaft coupling 42. The wear plate 37 is bored axiallyto enable it to be slipped over the inner section 62 of the coupling 42,suitably without bearing thereon. The rotor housing 4, the Wear plate 37and the main bearing housing 53 are secured together by suitable mainbearing housing screws 56, the wear I plate 37 being provided withsuitable ports through which the screws can pass with the plate thusbeing clamped between the housing 53 and the housing 4. Suitablegaskets, not shown, are preferably located under the heads of the screws56 to prevent leakage of fluid out of the apparatus around them.

The main bearing housing 53 is bored axially, the bore being adapted toprovide a seat for the outer race 50 of the main bearing 49. The extremeouter end of the bore of the main bearing housing 53 is dimensioned tofit rotatably the outer surface of the shaft coupling 42 which, as willbe apparent later, turns in the bore. Suitable means, such as a sealplate 47, a seal plate tensioning spring 43, a seal plate torque pin 44and a seal plate seal 46, are provided to prevent leakage of hydraulicfluid outwardly of the apparatus between the housing 53 and the coupling42. A suitable power take-off means, such as a belt pulley 52, or asprocket for a chain drive, is

secured, as by pulley screws 51, to the outer face of the housing 53, soas to rotate therewith around the coupling 42. In the modificationillustrated, suitable holes are provided in the bottom of the pulleyways which turn into register with the lockscrews 45 and through whichthe latter can be tightened, e.g. by means of a set screw wrench or ascrew driver.

The rotor housing 4 is of generally cylindrical interior configurationleaving a suitably thick wall except that the end of the housing nearestthe shaft coupling is provided with an apertured member, or end plate66, preferably formed as an integral part of the housing, which has alength, longitudinally of the housing, equal to that of the rotor 33.The character of the aperture in the plate 66 will be apparent from aninspection of FIGURES 4 and 5 and will be referred to later. Here itwill he noted only that the aperture is defined, in part, by a pair ofopposite arcuate surfaces 67 each of which in the assembled apparatus,is concentric with the longitudinal axis of the shaft coupling 42. Eachof the surfaces 67 is formed on a radius substantially the same as theradius of the outer surface of the rotor 33 so as to contact the lattersurface in sliding essentially liquid tight relationship. The surfaces67 have their centers diametrically opposite one another and extendthrough suitable equal arcs, e.g. by

way of example only, through arcs of roughly 65 to 75 degrees. Thesurfaces 67, can, for convenience, be referred to as concentric arcuatesurfaces.

An element of the driven assemblage comprises a second end plate 24which closes the end of the rotor housing 4, opposite the shaft coupling42. This end plate is usually inset into the end of the wall of therotor housing so as to be surrounded entirely by a flanged extension 78of the rotor housing. The end plate 24 is secured in place by suitableend plate screws, or bolts 26, and a suitable gasket or seal 9 isprovided between the flange and the end plate to prevent leakage offluid outwardly of the apparatus. the heads of the screws 26 to preventleakage of fluid out of the apparatus around the screws. The second endplate is provided with an elongated hub 79 which is located coaxiallywith the shaft coupling 42. The extreme inner end section 42 of the hub-79 is reduced in outer diameter and is adapted to seat on the innerrace 29 of the second bearing 30 referred to previously. An intermediategear seat section 83 of the hub 79 of somewhat greater external diameterthan the section 82 is adapted to receive an end plate gear 58, to bereferred to later, which is secured in place as by an end plate gear key10.

The end plate hub 79 is bored axially from its outer end to provide avalve plug'chamber 87, a valve chamber 84 of lesser internal diameterthan the chamber 87, a valve spring chamber 85 of lesser internaldiameter than the chamber 84 and a bleeder duct 86 of smaller diameterthan the chamber 85 which opens through the inner end of the hub. Thevalve comprises a valve body 88 of cylindrical exterior contour adaptedto slide snugly longitudinally in the valve chamber 84. One end of thevalve body, suitably its outer end, is provided with an encirclingfluid-conducting channel 89 through which fluid can flow around thebody. The valve body 88 is secured to, or is integral with, an elongatedvalve stem 92 which extends outwardly beyond the valve plug chamber 87.A suitable externally threaded valve plug 12 bored to receive the valvestem 92 slidably, is seated in the internally threaded valve plugchamber 87 to maintain the alignment of the valve stem. Suitable seals11 and 22 are conveniently provided to prevent leakage of hydraulicliquid outwardly of the apparatus between the valve plug and the wall ofthe valve plug chamber and between the valve plug and the valve stem,respectively.

The valve body is bored axially from its inner end to receive a suitablevalve spring 25, the other end of the spring being seated in the valvespring chamber 85. Normally the valve spring 25 is under compression andis conveniently a coil spring. The valve stem is also bored axially andis threaded internally near its outer end to receive an externallythreaded valve adjusting screw 18. The screw 18 bears at its inner endon a valve adjusting pin 21 and leakage of fluid outward around the pin21 is prevented by a suitable valve pin seal 55. The inner end of thepin 21 is provided with a pin plate 93 to Suitable gaskets, not shown,are located under bear on the end of the spring 25., It will thus beseen that, by adjusting the screw 18, the position of the plate 93 withrespect to the valve body 88 is adjusted inwardly or outwardly and thetension on the spring 25 is increased or decreased accordingly. Asuitable lock nut 19 can be provided to secure the adjusting screw 18against inadvertent manipulation. The driven assemblage thus comprisesthe rotor housing 4, including the apertured member 66, the second endplate 24 and integral hub 79 and the associated parts, together withother associated parts which will be referred to.

The configuration of certain of the parts and the manner of theircooperation will now be described in greater detail.

Intersecting the concentric arcuate surfaces 67 at their ends is anotherpair of arcuate surfaces 68, shown clearly in FIGURES 4 and 5, which arenonconcentric with the longitudinal axis of the shaft coupling 42, thepairs of surfaces 67 and 68 defining completely the aperture in the endplate 66. The two surfaces 68 have the same length as the two surfaces67 i.e. all four surfaces extend completely through the apertured member66. Each of the surfaces 68 is formed so that it is bisected by a radialline common to both extending at an angle of 90 degrees with respect toa line bisecting the two surfaces 67, both lines extending through theprolonged longitudinal axis of the shaft coupling 42. The radii of thetwo surfaces 68 are located at equal distances from, and on oppositesides of, the longitudinal axis of the shaft coupling 42. The surfaces68 are, for convenience, referred to as nonconcentric arcuate surfaces.

The rotor 33, as noted previously, and as is also apparent from FIGURES4 and 5, is a generally cylindrical element with a radius essentiallyequal to that of the two concentric arcuate surfaces 67. The rotor islocated within the aperture of the apertured member 66 and rotatestherein in essentially fluid tight contact with the concentric surfaces.It will be observed that the rotor clears the nonconcentric surfaces 68by a suitable distance leaving a crescent shaped channel, or fluidforwarding chamber, 77 between the rotor and each of the surfaces 68,the function of which will be apparent later. One end of the crescentshaped channel 77 is sealed against leakage of fluid therefrom by thewear plate 37 and the opposite end is similarly sealed by the rotorframe 5 which is of suflicient diameter adjacent to the apertured memberto cover completely the aperture therein.

The rotor is cut away from its outer surface to provide four arcuatesurfaces 69 extending the length of the rotor 33 with the radial centersof the surfaces being spaced equi-distantly around the rotor and witheach lying on a common are centered on the longitudal axis of the shaftcoupling and having a radius somewhat less than that of the outersurface of the rotor 33. The arcuate surfaces 69 thus extend througharcs of somewhat more than 180 degrees and define open-sided cavities 70which, for convenience may be referred to as rotor vane cavities or vanerotor chambers.

The valve body 88 which has been described functions to restrict theflow of hydraulic fluid in ducts provided in the driven assemblage ofthe apparatus. Referring to FIGURES 3, 4, 5 and 7 it will-be noted thatthe wall of the rotor housing 4 is formed, as by drillinglongitudinally, to provide a first rotor housing duct 99 extendinglongitudinally through it. The duct 99 communicates with an inlet, orfirst, port in the nonconcentric surface 68 by way of an inlet, orfi-rst, port duct, or slot, 98 milled longitudinally on the aperturedmember 66. One end of the duct 99 is closed by the wear plate 37. Theopposite end of the duct 99 communicates by way of a short registeringend plate duct 96 in the end plate 24 with a main end plate inlet duct97 drilled radially in the end plate -24. The duct 97 is closed at itsouter end by the flange 78 and communicates at its inner end with thevalve fluid channel 89 when the valve is adjusted suit- 9 ably. Therelationship of these several ducts, or first fluid-conveying ductsystem, with one another and with the valve fluid channel 89 is shown inFIGURE 7.

In similar manner the outlet, or second, port 76 of FIG- URES 4 and 5 inthe same nonconcentric surface 68 communicates by way of an outlet, orsecond, port duct, or slot, 95 in the apertu'red member 66 with a secondrotor housing duct ?9, not shown in FEGURE 3, in the rotor housing. Thelatter communicates by way of a short registering end plate outlet duct102 of FIGURE 7 with a radially formed main end plate outlet duct 106 inthe end plate 24, these several ducts comprising a second fluidconveyingduct system. Corresponding inlet and outlet duct systems extend betweenthe other nonconcentric surface 68 and the channel 89. It will beapparent that with the valve body 83 in its open position, i.e. at theextreme left in FIGURE 3, hydraulic liquid can flow freely by way of thefluid channel 89 between the systems of inlet and outlet ducts and thatwith the valve in this position any rotation of the driving assemblagewill merely serve to circulate fluid in the systems of ducts withoutexerting any appreciable force on the driven assemblage tending to causeit to rotate. When, on the other hand, the valve is in its Wholly closedposition, i.e. at the extreme right in FIGURE 3, the channel 89 is outof register with the ducts 97 and 16% and fluid is prevented in positivefashion from flowing between the inlet and outlet ducts. Under suchconditions the driving and driven assemblages become locked together andany rotation of the driving assemblage will cause an equal angularrotation of the driven assemblage. For intermediate positions of thevalve body 88, the flow of fluid through the fluid channel 89 will berestricted accordingly, but not prevented, and rotation of the drivingassemblage will cause rotation of the driven assemblage, but at a rateless than that of the driving assemblage in proportion to the degree towhich the flow of fluid is restricted. The inlet and outlet ports are,for best results, located at the extreme ends of the nonconcentricarcuate surfaces 68 and can, if desired, be located so that they arepartly, preferably to a minor extent, in the concentric'arcuate surfaces67.

As noted previously, four rotor vanes 2 are provided with each vanebeing located in a corresponding vane cavity in the rotor 33. Each vaneis integral with a rotor vane shaft 72 which is mounted in a suitablerotor vane bearing 6 extending through the rotor frame 5. Thelongitudinal axis of the shaft is co-extensive with the radial centerline of the corresponding vane cavity. Each rotor vane is formed with apair of opposed wings 73 and, as a matter of convenience, is formed withan enlarged, roughly cylindrical hub 74 which is, in effect, anextension of the shaft 72. Each Wing of each vane is of suitablethickness to provide the required strength and rigidity and is contouredat its outer end as a semi-cyclindrical surface, or vane tip, having aradius which is, for convenience, referred to as a vane tip radius,which will be referred to later, and which is generally equal to onehalf the thickness of the vane adjacent to the semi-cyclindn'calsurface. The extreme length of each vane from the center of onesemicylindrical vane tip surface to the other is twice the radius of thearcuate surfaces 69. Thus when a vane rotates about its axis of rotationwithin its vane cavity first one tip and then the other Wipes thesurface 69 in essentially fluid-tight relationship.

It is pointed out, further, that the four rotor vanes 2 are mounted andcontrolled as to their rotation, in a way which will be explained later,so that each extends at all times parallel, as determined by a linepassing through its vane tip radii, with a radial line common to boththe nonconcentric surfaces 68 and passing through the common axis ofrotation of the rotor 33, and of the apertured member 66. With a properdimensioning of the parts, it will be apparent, as shown clearly inFIGURES 4 and 5, that, as either the apertured member 66 or the rotor 33rotates with respect to the other, one tip of each vane ltd will Wipe anonconcentric surface 68 in fluid-tight relationship while the other tipof the vane is wiping the arcuate surface 69 in the same way. Thus,assuming the rotor 33 in FIGURE 5 to be rotating in a counter clockwisedirection and with an inlet port 75 for hydraulic fluid being providedat the end of a nonconcentric arcuate surface 68 first contacted by avane, as shown, a certain volume of hydraulic fluid will be trapped inthe space comp-rising the channel 77 andthe portions of the vanecavities 70 lying between the vane which has just passed the inlet portand the vane next ahead of it. This body of fluid will be transportedalong with the rotor and rotor vanes until the forward vane clears theedge of an outlet port 76, which is provided at the end of the samenonconcentric surface 68 opposite the inlet port 75. When the tip of theforward vane passes the edge of the outlet port 76, a portion of thetrapped fluid will be forced through the outlet port 76 as the rotor andvanes continue to rotate. An intermediate stage of this operation isillustrated in FIGURE 4 where it can be seen, as shown by arrows, thatfluidis being forced through the outlet port 76 by a vane at the sametime as an additional body of fluid is being drawn into the cavity andchannel behind the vane by way of the inlet port 75. In this way fluidis continually drawn from the inlet duct system into the cavity andchannel by way of the inlet port 75 and continually ported into theoutlet duct system by way of the outlet port 76.

In similar. fashion, and as the rotor and vane assemblage continue torotate, an additional quantity of fluid will be drawn through the secondinlet port 75 opposite the first into the corresponding vane cavity andchannel and will be forced therefrom through the outlet port 76 oppositethe first outlet port. It will be noted furthermore, that with eachcomplete rotation of the rotor and vane assemblage with respect to theapertured member 66 eight separate bodies of hydraulic fluid will beconveyed from an inlet port to an outlet port. Since each body of fluidthus conveyed is essentially equal to the volume of the crescent shapedfluid-forwarding chamber 77 and is considerably greater than the body offluid pumped during one rotation of a conventional gear pump ofcomparable size, it is clear that the capacity of the apparatus heredescribed for circulating fluid at a given rotational speed of operationis much greater than that of the comparable gear pump. This is ofconsiderable importance in that it furnishes a greater volume ofcirculating fluid and thus permits a much greater accuracy incontrolling the proportion of the fluid which is allowed to flow throughthe duct system between the outlet and inlet ports. By the same token agreater rate of fluid flow permits the building of the apparatus withless accurate manufacturing tolerance.

Referring again to FIGURES 4 and 5 it will be noted that the slidingcontact of the exterior cylindrical surface of the rotor 33 at all timesprovides a fluid tight seal with the concentric surface 67 between eachoutlet port and the inlet port ahead of it. There is thus little or nopossibility of fluid leaking backward with respect to the direction ofrotation of the rotor from one inlet port to the preceding outlet portwith a consequent loss in' inefliciency of the apparatus. It should alsobe pointed out that, as each vane travels between an outlet port and theinlet port next ahead of it, it is contained completely I within itscorresponding vane cavity. The hub of the vane may, for purposes ofstrength, he of sufficient diameter to pass near the concentric surface67 but it should I clear the surface by at least a small amount. It willbe 7 5 constantly varying capacity as the vane continues to rotate 1 7%within the vane cavity. The hub 74 should clear the concentric surface67 by a distance sufficient to allow a free interchange of fluid betweenthese two portions of the vane cavity.

It will also be observed, further, that the apparatus can be operatedwith equal efleotiveness should the rotor 33, as illustrated in FIGURES4 and 5, be caused to rotate in a clockwise rather than in acounter-clockwise direction. In this instance the inlet ports 75 becomeoutlet ports and the outlet ports 76 become inlet ports. The directionof rotation of the driven assemblage is, of course, reversed. It will benoted that, regardless of the direction of rotation of the rotor withrespect to the apertured member, the port in either nonconcentricarcuate surface encountered first by a rotor vane, and the part of theduct system extending between that port and the valve chamber, arereferred to as the inlet, or first port and the inlet," or first ductsystem whereas the other port in the same nonconcentric arcuate surface,and the part of the duct system extending between it and the valvechamber, are referred to as the outlet, or seeon port and the outlet, orsecon duct system.

The necessity of maintaining certain relationships between thedimensions of the parts for best results has been mentioned. Although itis believed that these are apparent from the description thus far given,certain of them may be mentioned again to advantage.

It will be clear that the capacity of the apparatus to circulatehydraulic fluid in the duct system will be related directly to thelength of the rotor vanes measured from the center of onesemi-cylindrical tip surface to the other along a line normal to andintersecting the axis of rotaton of the vane. Thus, the longer the vane,the

greater will be the capacity of its vane chamber 70, and

of the crescent shaped channel 77, and, correspondingly, the volume offluid circulated per unit time for a given rotational speed of the rotor33 with respect to the apertured member. As mentioned previously, anadequate provision for circulation of fluid is desirable.

The radius of the vane chamber, should, from an inspection of FIGURES 4and 5, clearly be equal to one half the extreme length of the vane, i.e.to the distance from the axis of rotation of the vane to the center ofone of its semi-cylindrical tip surfaces, and this distance should, inturn, be equal to the distance from the center of rotation of the vaneto the midpoint of the nonconcentric arcuate surface 68 measured along aline intersecting the common axis of rotation of the rotor and of theapertured member. To insure continuous wiping of the nonconcentricarcuate surface 68 throughout its length by the vane tip, the radius ofthe surface 68 should be equal to the distance between the axis ofrotation of the vane and the axis of rotation of the apertured memberplus the vane tip radius. It should, of course, be located on a lineconnecting the midpoint of the surface 68 and the axis of rotation ofthe apertured member.

To provide for easy shifting of the valve body 88 in the valve chamber84, a small drain duct 106 is drilled in the valve body to providecommunication between the parts of the chamber on opposite sides of thebody. The duct 86 permits free flow of fluid between valve chamber 84and the interior cavity 107 of the apparatus. The latter cavity servesas a reservoir for hydraulic fluid, generally a lubricating oil, for theintroduction of which a convenient and conventional filler plug 108 canbe provided in the wall of the rotor housing 4.

The end plate gear 58, the idler gear 28 and the rotor vane gear 7 havebeen referred to previously. The relationship and manner of cooperationof these gears is shown in FIGURE 6. As noted previously, the end plategear 58 is secured, as by a keq 10, to the intermediate section 83 ofthe hub 79 and rotates therewith. The gear 58 meshes with a pair ofoppositely located idler gears 28 mounted on the idler gear bolts 35,suitably by way of anti-friction bearings 27, the bolts having beendescribed previously. Each idler gear 28 lies between and meshes onopposite of its sides with a pair of rotor vane gears 7, each of whichis secured, as by a key 54, to its respective rotor vane shaft 72, therebeing four rotor vane gears and shafts in the modification illustrated.The gear 5 8 and the four gears 7 have the same number of teeth and eachidler gear conveniently has the same number of teeth as the other. Itwill thus be seen that any rotation of either the rotor frame 5, onwhich the vane shafts 72 are mounted, or the intermediate sections 83 ofthe hub 79 with respect to one another will cause each of the fourshafts 72 to rotate in their bearings at the same rate and in the samedirection. Furthermore, the rates of rotation of the shafts 72 will beat the same rate and in the same direction as those of the end plategear 58, i.e. in the same direction and at the same angular rate as theapertured member 66.. Under such conditions, and with each rotor vane 2originally assembled with its cross sectional axis, i.e. its axis whichpasses through the vane ti-p radii normal to its longitudinal axis,extending parallel with a line passing through the radial centers of thetwo nonconcentric surfaces 68, this same relationship will be preservedregardless of the rotations of the driving assemblage and of the drivenassemblage with respect to one another, and the proper wiping action ofthe vane tips on the surfaces 68 and 69 mentioned previously will beeffected.

The adjustment of the valve body 83 in the valve chamber to regulate therotational speed of the driven assemblage can be elfected in anyconvenient manner either manually or automatically, as desired. In apreferred modification the valve stem 92 can be provided with a groovedcollar mounted rotatably thereon to avoid rotational contact of thevalve body 88 and the wall of the valve chamber 84. One suitable groovedcollar illustrated in FIGURE 3 comprises a rear retainer plate 29 and afront retainer plate 15 secured together with retainer screws 16 andmounted rotatably on the valve stem by way of ball bearings 17. Theperipheries of the facing surfaces of the retainer plates are cut awayto form a retainer plate channel or groove 1G9 around the collar.

A suitable valve adjusting member can be positioned to ride in thechannel 199 and connected to, and manipulated manually by, suitablelever means, not shown, to effect retraction and advancement of thevalve body 88. The lever means can, of course, be mounted on a supportseparate from the rest of the power transmitting device.

In the modification illustrated .in FIGURES 1, 2 and 3, means areprovided for controlling the location of the valve body 83 in the valvechamber 84 automatically to cause the driven assemblage to rotate atconstant predetermined speed. In this modification the outer end of thehub 79 protrudes outwardly ofthe end plate 24 and is threaded externallyto receive an internally threaded control collar 111 which is secured inplace as by a control collar set screw 112. Opposed pairs of angularlyextending regulator supporting arms 113 are secured, as by controlsupport screws 114,-to flat surfaces formed on the sides of the collar111. Alternatively the collar 111 and the arms 113 can be formed, e.g.by casting, integral with one another. Each pair of supporting arms 113provides a mounting for a fly weight pivot pin 14 which extends betweenthe arms and serves as a pivot for a fiy weight mounted thereon, eachfly weight comprising a pair of angular arms to the end of one of whicha valve adjusting member 110 is secured and to the end of the other ofwhich is secured a suitably heavy weight 115. Rotation of the drivenassemblage, including the collar 111 and arms 113, causes the flyweights to rotate on the pivot pins 14 by the action of centrifugalforce on the weights until further rotation is prevented by theincreased tension on the valvespring 25. When this stage is reached, thedriven assemblage will continue to rotate at constant speed, the actualvalue of which will depend upon the presetting of the valve adjustingscrew 18. Other suitable 13 means for controlling the output speed ofthe power transmitting device can beemployed.

It will be appreciated that when the apparatus described is operatedwith the fluid-restricting valve partly or completely open, a number ofinstances occur where one sunface slides on or wipes another surface.The wiping of the arcuate surfaces 69 and the nonconcentric arcuatesurfaces 63 by the tips of the rotor vanes 2 has been noted. It willalso be apparent that one end of each rot-or vane wipes the face of therotor frame 5 as it rotates while the other end of the vane wipes thewear plate 37. Also, one end of the rotor 33 is in sliding or wipingcontact with the wear plate; Since the apparatus is normally operatedusing a hydraulic liquid, the manufacturing tolerances of the surfacesmaking such contacts need be only sufficient to insure a satisfactoryhydraulic liquid seal. In fact, it is preferred that the sliding orwiping surfaces travel close to one another but that they avoid, insofaras is conveniently possible, any actual bearing on one another. Thiscontributes to economy of manufacture of the apparatus and minimizeswear during its use.

It has been mentioned that a filler plug 108- is conveniently providedin the rotor housing by way of which hydraulic fluid can be introducedinto the reservoir chamber 107. It is convenient to provide a suitablemeans, such as the check valve assemblage illustrated at 60 of FIGURE 3,for passage of fluid from the reservoir 7 into the inlet part of theduct system, this part of the system not ordinarily being underpressure. Once the reservoir 1u7'is filled with oil and the apparatusrun slowly for a short time, especially with the fluid-restricting valve7 To insure the best balancing of the apparatus it is usual practice toprovide a separate check valve assemblage 60 communicating with theinlet part of the duct system leading to each vane chamber. The ducts 94and 99 extending longitudinally of the rotor housing wall, shown clearlyin FIGURE 6, are preferably located symmetrically around the wall toprovide .proper balancing of the housing. It should be noted, further,that the entire apparatus involves no reciprocating parts which travelat high speed and that each rotational part is easily adaptable toaccurate balancing. The entire apparatus when carefully mde runssmoothly and quietly and with a high degree of efficiency.

Certain modifications of the apparatus of'the invention adaptedparticularly to use for purposes other than as a variable speed powertransmitting device will now be described.

In the modification of FIGURE 8 the apertured member 66 is clampedbetween an outlet housing 116 and an inlet housing 117, e.g. by suitablebolts, not shown. The subassernbly thus formed is mounted rigidly onsuitablesupports, e.g. as by brackets 147 on piers 146. The inlethousing 117 is provided with a threaded housing inlet port 113 and theoutlet housing 116 is provided with a threaded housing outlet port 119for connection to supply and delivery conduits, respectively. The endsof the aperture in the apertured member 66 are secured against leakageof fluid by a pair of seal plates 121 and 122 which are clasped tightlyagainst the ends of the rotor 33 in sliding fluid-tight relationshipwith the ends of the apertured member 66 by suitably shouldered idlergear bolts and bolts 30 so as to rotate with the rotor. It will be seenthat using this modification a fluid can be pumped by way of the outletport 119 to a desired location when the rotor 14 is rotated in theproper direction, but that when the direction of rotation of the rotoris reversed, fluid will be drawn into the apparatus by way of the port119 and delivered by way Of the port 118, the apparatus thus beingcompletely reversible.

In FIGURE 9 there is illustrated a modification having threefluidfor-warding chambers, or crescent shaped channels, 77, six rotorvane chambers 70, a triangular rotor vane 123 having three rotor vanetips 124 located in each rotor vane chamber. In this instance aparticular vane tip of each vane wipes the same non-concentric arcuatesurface once during each revolution of the apertured member 66, or ofthe rotor 33, with respect to the other.

In FIGURE 10 there is illustrated a modification having fourfluid-forwarding chambers 77 and eight rotor vane chambers 70 with asquare rotor vane 125 in each rotor vane chamber. Each rotor vane hasfour rotor vane tips 126. Here again a particular rotor vane tip of eachrotor vane wipes the same non-concentric arcuate surface 66 during eachrevolution of the apertured member 66, or of the rotor 33 with respectto the other.

In the modification of FIGURE 11 the end plate gear, corresponding tothe end plate gear 58 of FIGURE 3, is replaced with a cam eccentric 127which is mounted rigidly, but off center, with respect to the aperturedmember shown in outline at 66. A cam plate 128 is mounted concentricwith, and rotatably on, the eccentric. Each rotor vane chamber 70, shownmostly in dotted outline, contains a rotor vane which is provided withan offset drive pin 129 which is secured in rotatable fashion in the camplate at a predetermined distance from its center. The parts aredimensional to insure that upon rotation of the apertured member, or ofthe rotor, not shown, with respect to the other, each rotor vane rotatesin its respective rotor vane chamber at the required rate.

In the modification of FIGURE 12 a portion 131 of each nonconcent-ricarcuate surface 68 and a portion 135 of the wall 69 of each rotorvanechamber 70 is adjustable to permit controlled bypassing of fluid pastthe ends of the rotor vanes for regulating the relative rotationalspeeds of the apertured member 66 and the rotor 33. In this modificationthe portions 130 of the nonconcentric surfaces 68 are each formed on anapertured member in sert 131 separate from the apertured member 66 butretained therein in suitable insert raceways 137. The inserts areadapted to be moved radially of the rotor 33 inwardly of the apparatusuntil the surface 130 is continuous with the surface 68 and is in aposition to be wiped positively with the appropriate vane tip or to bemoved radially of the rotor outwardly of the apparatus until the surface130 clears the vane tip by a predetermined distance. In this latterposi-tion a part of the fluid flowing .through the fluid-forwardingchamber 77 flows past the vane tip and the difference in relativerotational speeds of the apertured member arid the rotor is increased.Although the adjustment of the members 131 can be effected in anyappropriate manner, there are shown in the illustration adjusting. bolts132 running in threaded ports in the apertured member 66 which preventthe inserts 131 from moving too far outwardly in response to thepressure of fluid in the fluid-forwarding chamber 77. Suitable shoulders133 can be provided to prevent the members 131 from moving so farinwardly that they will interfere with the proper movement of the rotorvanes 2.

Rotor insert members 134 can also be provided which travel radially ofthe rotor in rotor insert raceways 138 in the rotor 33. The outer end ofeach insert 134 is- By retractrotor vane. Control of the positions ofthe rotor inserts 134 in their raceways 138 can be effected in anyconvenient manner. In the illustration given, the member 140 representsa suitably mounted adjustable conical cam element coaxial with the rotor33. By adjusting the cam element 130 longitudinally of the axis of therotor, the

rotor inserts 134, which ride on the cam surface, as at 148, areadjusted radially inward or outward of the rotor.

The positions of the inserts 131 and 134 when allowing no bypassing offluid is shown clearly in FIGURE 12 in which the arcuate surfaces 139and 135 of the inserts are shown in a position to be wiped positively bythe vane tips. When, however, both inserts 131 and 134 are re-' tractedin their respective directions so that the surfaces are cleared anappreciable distance by the vane tips, bypassing of fluid past themoccurs. This condition is shown clearly in FIGURE 13 where the diameterof the cam element 140 with respect to the dimensions of the other partsis seen to be less than in FIGURE 12, the tapered surface of the cam 140being shown at 149. In practice either or both of the inserts can beretracted. In a further modification, not shown, a suitable fluid, suchas a hydraulic liquid or, in some instances, a gas, can be admitted tothe raceways 137 and 138 behind the inserts 131 and 134. By metering theamount of fluid ad mitted to each raceway the positions of therespective inserts can be adjusted and maintained constant. By arrangingfor the amount of metered fluid contained in the raceways to beinversely responsive to the rotational speed of one of the assemblages,the speed of that assemblage can be maintained essentially constantregardless of the speed of the other assemblage.

In FIGURE 14 there is illustrated a modification having a single rotorvane 2, a single rotor vane chamber or cavity 70 and a singlefluid-forwarding chamber 77. In this instance suitable inlet and outletcheck valves 139 and 141, respectively, are installed in the inlet andoutlet duct systems 142 and 143, respectively, to restrict the flow offluid in chamber 77 to one direction only, the rotation of the rotor 33for the setting of the check valves shown being in the directionindicated by the arrow. In the event it is desired to forward fluid inthereverse direction, the check valves 139 and 141 are reversed and therotor is rotated in the opposite direction from that shown, the ductsystem 143 then becoming the inlet duct system and the duct 142 becomingthe outlet duct sys-- tem. In the event a positive forward motion offluid, followed by a return flow, is desired, the check valves 139 and141 can be omitted.

Any suitable means, such as a gear train or a cam arrangement resemblingthose discussed previously, is provided, but not shown in FIGURE 14, tocause rotation of the rotor vane 2 in the rotor vane chamber 70 in thesame direction and at the same rate at which the apertured member 66rotates with respect to the rotor 33. Since in this instance, as well asin certain other instances, e.g. as in the modification of FIGURE 8, itis more con venient, to facilitate the connecting of fluid-conveyingconduits to the inlet and outlet duct systems, to provide means toprevent any rotation of the apertured member, such as lugs 151 and bolts152, it is sometimes more appropriate, but equivalent, to express thegeneral relationship of the rotation of the parts by stating that therotor vane.2 rotates in its chamber 70 at the same rate as, but in thereverse direction of, that of the rotor 33 with respect to the aperturedmember 66.

In FIGURE 14 it will be noted that when the rotor 33 is rotated throughan angle of 180 degrees from its position illustrated, the rotor vane 2will again be protruding beyond the circumference of the rotor 33. Toprovide room for clearance of the vane, a suitable clearance chamber 144can be provided in the apertured member opposite the chamber 77 anddimensioned to prevent entirely any contact of the vane with the wall ofthe chamber. Under such circumstances, and with adequate dimensions ofthe clearance chamber, each rotation of the rotor forwards a preciselymeasured amount of fluid through outlet conduit 143 with no furtherforwarding of fluid until the next time the rotor vane enters the fluidforwarding chamber 77. To avoid wastage of, or contamination of, thefluid being forwarded, the chamber 144 is closed and filled with thefluid being forwarded. With the chamber 144 in communication by way of asuitable pressure equalizing conduit 145 with the outlet conduit 143,leakage of fluid past the rotor from the fluid-forwarding chamber 77into the clearance chamber 144 is minimized.

It will be apparent that the apparatus of FIGURE 14 is thus adapted tofurnish a pulsed flow of fiuid in the outlet conduit 143. It will belikewise apparent without further illustration that by providing asecond rotor vane chamber and corresponding rotor vane in the rotor 33opposite the chamber and vane illustrated, a pulsed flow of fluid can beproduced to which the pulse rate is, for the same rate of rotation ofthe rotor, twice that produced with a single vane. Also by forming theclearance chamber 144 as an actual fluid-forwarding chamber opposite to,and with identical dimensions as, the chamber 77, the pulse rate can bedoubled while still employing a single vane. It is, of course,understood that in this, as well as in other, modifications of theinvention including a plurality of fluid-forwarding chambers, the inletports of all of the chambers are in many instances connected to the sameinlet duct system and the outlet ports of all of the chambers areconnected to the same duct system.

Multiple function effects can be obtained by constructing the apparatuswith two or more apertured members as elements of the second assemblageand a corresponding number of rotors and associated parts as elements ofthe first assemblage and by arranging the duct systems to provide forone apertured member and the corresponding rotor and vane assemblage toperform one function while another apertured member and its associatedrotor and vane assemblage is performing another function.

The foregoing remarks and an inspection of the drawing lead to certainconclusions concerning the preferred form of the invention when theapparatus is constructed to insure the rotation of the rotor vane in therotor vane chambers in the same direction as, and at the same rate as,the relative rotation of the apertured member with respect to the rotor.Under such circumstances the number of vane tips on each rotor vane canwith advantage be at least as great as, and preferably, except in thecase of a single chamber, equal to, the number of fluidforwardingchambers. It has been pointed out that the nonconcentric surface of anyparticular fluid-forwarding chamber is ordinarily, and preferably wipedin turn by a particular tip of each succeeding vane and that this tipdoes not wipe the nonconcentric surface of any other fluid-forwardingchamber.

It should, however, be pointed out that this is not always necessarilythe case. Thus, for example, the apparatus can comprise fourfluid-forwarding chambers located symmetrically in the apertured memberand eight rotor vanes in eight rotor vane chambers located symmetricallyaround the rotor, the rotor vane in each,vane chamber having twodiametrically opposed vane tips with the vane diameters extendingbetween the tips of alternate vanes being located at right angles withrespect to the vane diameters extending between the tips of theintervening vanes. In such instance the respective tips of alternatevanes wipe the nonconcentric arcuate surfaces of one pair of opposedfluid-forwarding chambers while back flow of fluid can occur in theother pair of opposed chambers. Subsequently, the respective tips of theintervening vanes wipe the nonconcentric arcuate surfaces of the otherpair of opposed chambers while back flow of fluid through the first pairof chambers can occur. By

17 the installation of suitable check valves, the back flow of fluidreferred to can, of course, be prevented.

It is also pointed out that in the modification just referred to it isfeasible to form one opposed pair of fluid-forwarding chambers and theappropriate set of vane chambers and rotor vanes with somewhat differentdimensions than those of the other fluid-forwarding chambers, rotor vanechambers and rotor vanes. This provides for forwarding a fluid at onerate through one opposed pair of fluid-forwarding chambers and at adifferent rate through the other pair. This modification is useful forproviding a pulsed continuous flow of. fluid.

In another variation of the foregoing arrangement each rotor vane can beprovided with four vane tips, rather than with two, locatedsymmetrically around it, in which case a tip of each vane will wipe aparticular nonconcentric arcuate surface. In this instance it will benoted that as one vane closes an inlet port and another vane begins toopen an outlet port of the same fluidforwarding chamber, an interveningvane midway between them will also be wiping the nonconcentric arcuatesurface. This modification is of particular value when the apparatus isused to compress a gas since the presence of the intervening vaneassists materially in preventing blow-by of gas past the vane tips.

When the use of check valves in the inlet and outlet duct systems toprevent back flow of fluid through the fluid-forwarding chambers is tobe avoided, it is essential that the inlet port for eachfluid-forwarding chamber be closed completely by an advancing rotor vanebefore the vane ahead of the advancing vane begins to open the outletport for the same chamber. Thus, the radial angle between adjacent rotorvanes should in this instance not be greater than the radial anglebetween the edges nearest one another of the inlet and outlet ports foreach fluid-conveying chamber, both angles being measured with the commonaxis of rotation of the rotor and of the apertured member as a center.

The apparatus of the invention has been described with particularreference to the nonconcentric arcuate surfaces as forming a part of thesurface of the aperture of the apertured member in which case the inletand outlet ports and the corresponding fluid-conveying duct systems areassociated with the apertured member and the rotary va'ne chambers androtor vanes are associated with the rotor. Although not illustrated inthe drawing, it is also feasible, but not usually as convenient, to formthe vane chambers in the apertured member and to form the nonconcentricsurfaces as sections of the surface of the rotor. In such an instancethe aperture of the apertured member is entirely cylindrical exceptwhere it is interrupted by openings to provide for the communication ofthe vane chambers with the fluidforwarding chambers. The nonconcentricsurfaces are formed on the rotor as arcs of greater radius than that ofthe rotor and intersect the cylindrical intermediate sections of thesurface of the rotor at their ends, the crescent shape fluid-forwardingchambers being defined by the nonconcentric surfaces on the face of therotor and the concentric surface of the aperture of the aperturedmember. The inlet and outlet ports are formed in the nonconcentricsurfaces near their ends and the inlet and outlet fluid-conveying ductsystems are formed, e.g. by drilling, within the body of the rotor.Communication of the fluid-conveying duct systems with conduits outsidethe apparatus can be by any suitable means, e.g. by way of alongitudinally drilled axial shaft and suitable outside connections. Themeans for rotating the rotor vanes in the rotor vane chambers, such as aset of meshing gears or a suitable cam arrangement, is, in thisinstance, arranged to cause each vane to rotate in its vane chamber inthe same direction as, and at the same rate as, the relative rotation ofthe rotor with respect to the apertured member.

I claim:

1. In a fluid power apparatus comprising first and second assemblages ofmembers, the combination including:

a rotatably mounted apertured member of predetermined length associatedwith the second assemblage wherein the aperture is defined, in part, byat least one arcuate surface concentric with the axis of rotation of theapertured member, and in part, by at least one arcuate surfacenonconcentric with the axis of rotation of the apertured member, theconcentric and nonconcentric surfaces intercepting one anotherlongitudinally of the aperture;

a first fluid-conveying duct system in the second assemblagecommunicating with a first fluid port located at least partially in oneend of a nonconcentric arcuate surface adjacent to a concentric surface;

a second fluid-conveying duct system in the second assemblagecommunicating with a second fluid port located in the opposite end ofthe same nonconcentric surface adjacent to a concentric surface;

a rotor of generally cylindrical configuration associated with the firstassemblage having a length essentially equal to that of the aperture ofthe apertured member and having a radius essentially equal to that ofthe concentric arcuate surface, the rotor being located within theapertureofthe apertured member and being rotatable relative to theapertured member with its exterior surface in substantially fluid-tightrelationship with the concentric arcuate surface, but spaced from thenonconcentric arcuate surface by a predetermined distance to define afluid-forwarding chamber between the rotor and the nonconcentric arcuatesurface;

a rotor vane chamber of incomplete cylindrical contour with a radiusless than that of the rotor inset into the cylindrical surface of, andaxially parallel with, the rotor with a side opening through the rotorsurface facing the wall of the aperture in the apertured member; g

a rotor vane having a length essentially equal to that of the apertureof the apertured member located rotatively in the rotor vane chamberwith its rotational axis coincident with the radial center of the rotorvane chamber and formed with at least two vane tips each extendingparallel with the rotational axis of the vane and distant therefrom by adistance essentially equal to the radius of the rotor vane chamber;

means to close both ends of the aperture of the apertured member toprevent essentially the flow of fluid from the ends of the apertureduring relative rotation of the first and second assemblages withrespect to one another; and

vane rotating means responsive to the relative rotation of the first andsecond assemblages with respect to one another to cause rotation of therotor vane within the rotor vane chamber to cause one of its tips towipe the surface of the rotor vane chamber, the parts being dimensionedto cause another of its tips to wipe simultaneously. a nonconcentricarcuate surface.

2. Apparatus as claimed in claim 1 wherein means is provided to rotateone of the assemblages with respect to the other.

3. Apparatus as claimed in claim 1 wherein the vane rotating meanscomprises a first gear mounted on and rotatable with, a rotor vane, asecond gear mountedon, and rotatable-with, the second assemblage and anidler gear mounted on a spindle secured on the rotor and meshing withthe first and second gears.

4. Apparatus as claimed in claim 1 wherein the numbers offluid-forwarding chambers and the number of rotor vane chambers and ofrotor vanes are each more than one and each rotor vane comprises anumber of rotor vane tips equal to the number of fluid-forwardingchambers.

5. Apparatus as claimed in claim 4 wherein the radial angle, measuredwith the rotational axis of the rotor as a center, between adjacentrotor vanes is not greater than the radial angle, measured from the samecenter, between the edges nearest one another of the inlet and outletports of a fluid-forwarding chamber.

6. Apparatus as claimed in claim 4 wherein the first and secondfluid-conveying duct systems are connected to one another and a fluidflow restricting means is located in the path of fluid flowing in theconnected duct systems and wherein means is provided to rotate one ofthe assemblages with respect to the other.

7. In a variable speed hydraulic power transmitting device comprisingdriving and driven assemblages of members wherein the driving assemblageincludes elements for forwarding a hydraulic fluid through a system offluid conveying ducts in the driven assemblage and wherein the drivenassemblage includes valve means for restricting the flow of hydraulicfluid in the system of fluid conveying ducts, the combination including:

a rotatably mounted apertured member of predetermined length associatedwith a driven assemblage wherein the aperture is defined, in part, by apair of diametrically opposed concentric arcuate surfaces of equalradius each concentric with the axis of rotation of the aperturedmember, and, in part, by a second pair of diametrically opposednonconcentric arcuate surfaces of equal radius intersecting theconcentric arcuate surfaces, the radial centers of the nonconcentricarcuate surfaces being located at equal distances on opposite sides ofthe axis of rotation of the apertured member and the centers of thealternating concentric and nonconcentric arcuate surfaces being disposedat angles of 90 degrees from one another with respect to the axis ofrotation of the apertured member;

a system of fluid conveying ducts in the driven assemblage communicatingwith a port located at least partially in each nonconcentric surfaceadjacent to each intersection thereof with a concentric surface;

a rotor of generally cylindrical configuration associated with thedriving assemblage having a length essentially equal to that of theapertured member and having a radius essentially equal to that of theconcentric arcuate surfaces, the rotor being located within the apertureof the apertured member and being rotatable coaxially with the memberwith its exterior surface in sliding fluid tight relationship with theconcentric arcuate surfaces, but spaced from the nonconcentric arcuatesurfaces by a predetermined distance;

a series of four rotor vane chambers of arcuate surface contour insetinto the cylindrical surface of the rotor, each chamber being ofincomplete cylindrical configuration with a side opening through therotor surface facing the wall of the aperture in the apertured memberand the radial centers of the chambers being parallel with, equidistantfrom and spaced at equal angular distances around the axis of rotationof the rotor at a distance therefrom less than the radius of the rotor;

a rotor vane having a length essentially equal to the length of therotor located rotatably in each rotor vane chamber with its longitudinalrotational axis coincident with the radial center of the chamber andwith its longest cross sectional axis, normal to its rotational axis,extending parallel with a line connecting the .radial centers of thenonconcentric surfaces;

means to close both ends of the aperture in the apertured member torestrict the flow of hydraulic fluid from the ends of the aperture; and

means responsive to the relative rotation of the rotor and the aperturedmember with respect to one another to cause rotation of each rotor vanein its cham- 20 her in the same direction and to the same angular extentas the apertured member.

8. Apparatus as claimed in claim 7 wherein the parts are dimensioned tocause one tip of each vane to wipe in fluid tight relationship thearcuate surface defining the corresponding vane chamber, during therotation of the rotor and the apertured member with respect to oneanother, and to cause the opposite tip of the vane simultaneously towipe in fluid tight relationship oneof the nonconcentric arcuatesurfaces.

Apparatus as claimed in claim 7 wherein each tip of each vane is formedas a semi-cylindrical surface with a vane tip radius equal to one halfthe thickness of the vane adjacent to the tip.

10. Apparatus as claimed in claim 7 including a suitable end plate gearrotatable with the driven assemblage, a suitable rotor vane gearrotatable with each rotor vane, the end plate gear and the rotor vanegears each having the same number of teeth, and'idler gears meshedbetween the end plate gear and the rotor vane gears whereby each rotorvane is caused to rotate in its respective vane chamber in the samedirection and to the same angular extent as the apertured member.

11. Apparatus as claimed in claim 7 including bearing means whereon thedriving and driven assemblages are mounted to rotate coaxially with oneanother.

12. In a variable speed hydraulic power transmitting device comprisingdriving and driven assemblages of members wherein the driving assemblageis adapted to be connected to a power input source and wherein thedriven assemblage is adapted to be connected as a power output source,the combination including:

a-rotor housing of generally cylindrical configuration rotatable on itslongitudinal axis associated with the driven assemblage closed at one ofits ends with an end plate having an axially disposed elongated hub;

an apertured member concentric with the longitudinal axis of theelongated hub closing the opposite end of the rotor housing except foran aperture therein defined, in part, by a pair of arcuate surfaces eachconcentric with the rotational axis of the apertured member and, inpart, by a pair of diametrically opposed nonconcentric arcuate surfacesof eqaul radius intersecting the concentric arcuate surfaces, the radialcenters of the nonconcentric arcuate surfaces being located at equaldistances from, and on opposite sides of, the rotational axis of theapertured member and the center of the alternating concentric andnonconcentric arcuate surfaces being disposed at angles of degrees fromone another with respect to' the axis of rotation of the aperturedmemher;

a duct system including inlet duct parts and outlet duct parts locatedin the apertured member, the wall of the rotor housing and the endplate, each part of the duct system communicating at one of its endswith a valve chamber located in the elongated hub and at its other endwith a port located at least partially in each nonconcentric arcuatesurface adjacent to an intersection thereof with a concentric arcuatesurface;

a valve means located in the valve chamber adapted to restrict inpredetermined manner the flow of hydraulic fluid through the valvechamber between the inlet and outlet ports of the system;

a wear plate rotatable with the apertured member closing the end of theaperture opposite the end plate;

power takeoff means secured to the rotor housing opposite the end plate;

a power input shaft coupling associated with the driving assemblageadapted to be connected to a source of power;

an axially bored rotor secured to, and rotatable coaxially with, theshaft coupling of generally cylindrical configuration of essentially thesame length as the apertured member located rotatably within theaperture concentric with, and in essentially fluid tight relationshipwith, the pair of concentric arcuate surfaces, the end of the rotoradjacent to the Wear plate being in rotational sliding essentially fluidtight relationship therewith;

a generally circular rotor frame secured to the end of the rotoroppositethe wear plate having a diameter greater than that of the aperture inthe apertured member rotatable with the rotor and in rotational Slidingessentially fluid tight relationship with the apertured member entirelyaround the aperture;

a series of four rotor vane chambers of arcuate surface contour insetinto the cylindrical surface of the rotor, each chamber being ofincomplete cylindrical configuration with a side opening through therotor surface facing the wall of the aperture inv the apertured memberand the radial centers of the chambers being parallel With, equidistantfrom and spaced at equal angular distances around the axis of rotationof the rotor at a distance therefrom less than the radius of the rotor;

a rotor vane having a central hub and oppositely extending vanesintegral therewith located rotatably in each rotor vane chamber with itslongitudinal rotational axis coincident with the radial center of thechamber and with its axis measured from one vane tip to the other normalto its axis of rotation extending parallel with a line connecting theradial centers of the nonconcentric arcuate surfaces, each vane tipsurface being of semicylindrical configuration formed on a vane tipradius, each rotor vane having an axial shaft mounted rotatably in asuitable bearing in the rotor frame and the ends of each vane bearing inrotational sliding essentially fluid tight relationship on the wearplate and on the rotor frame, respectively;

an end plate gear secured to and rotatable with the end plate hub;

a rotor vane gear having the same number of teeth as the end plate gearsecured to and rotatable with each rotor vane shaft; and

idler gears mounted rotatably on shafts in fixed location with respectto the rotor meshing with the end plate gear and with the rotor vanegears whereby, upon rotation of either the driving assemblage or thedriven assemblage with respect to the other, each rotor vane is rotatedin its respective vane chamber in the same direction and to the sameangular extent as the apertured member, the parts being dimensioned tocause one tip of each vane to wipe in essentially fluid tight manner thearcuate surface defining its respective vane chamber while the other tipof the vane is wiping one of the nonconcentric arcuate surfaces in thesame manner.

13. In a variable speed hydraulic power transmitting device comprisingdriving and driven assemblages of members wherein the driving assemblageincludes elements for forwarding a hydraulic fluid through a system offluid conveying ducts in the driven assemblage and wherein the drivenassemblage includes valve means for restricting the flow of hydraulicfluid in the system of fluid conveying ducts, the combination including:

a rotatably mounted apertured member of predetermined length associatedwith the driven assemblage wherein the aperture is defined, in part, byat least one pair of diametrically opposed concentric arcuate surfaces,each concentric with the axis of rotation of the apertured member, and,in part, by at least one pair of diametrically opposed nonconcentricarcuate surfaces of equal radius intersecting the concentric arcuatesurfaces, the radial centers of the nonconcentric arcuate surfaces beinglocated at equal distances from the axis of rotation of the aperturedmember and the centers of the alternating concentricand nonconcentricarcuate surfaces being disposed at equal angles from one another withrespect of the axis of rotation of the apertured member;

a system of fluid conveying ducts in the driven assemblage communicatingwith a port located at least partially in each nonconcentric surfaceadjacent to each intersection thereof with a concentric surface;

a rotor of generally cylindrical configuration associated with thedriving assemblage having a length essentially equal to that of theapertured member and having a radius essentially equal to that of theconcentric arcuate surfaces, the rotor being located within the apertureof the apertured member and being rotatable coaxially with the memberwith its ex terior surface in sliding fluid tight relationship with theconcenric arcuate surfaces, but spaced from the nonconcentric arcuatesurfaces by a predetermined distance;

a series of'rotor vane chambers of arcuate surface contour equal innumber to the number of nonconcentric surfaces, each chamber being insetinto the cylindrical surface of the rotor and being of incompletecylindrical configuration with a side opening through the rotor surfacefacing the wall of the aperture in the apertured member, the radialcenters of-the chambers being parallel with, equidistant from and spacedat equal angular distances around the axis of rotation of the rotor at adistance therefrom less than the radius of the rotor;

a rotor vane having a length essentially equal to the length of therotor located rotatably in each rotor vane chamber with its longitudinalrotational axis coincident with the radial center of the chamber andwith its longest cross-sectional axis, normal to its rotational axis,essentially equal to twice the radius of the rotor vane chamber;

means to close both ends of the aperture of the apertured member torestrict the flow of hydraulic fluid from the ends of the aperture; and

means responsive to the relative rotation of the rotor and the aperturedmember with respect to one another to cause rotation of each rotor vanein its chamber in the same direction as'the apertured memher and at apredetermined angular speed with respect to the angular speed of theapertured member.

References Cited by the Examiner UNITED STATES PATENTS 2,379,592 7/1945Philbrick 192- 5s 2,816,637 12/1957 Bucherer "192-58 2,907,429 10/1959Selden 192 5s 7 2,939,560 6/1960 Selden 192-5s FOREIGN PATENTS 630,77911/1961 Canada.

DON A WAITE, Primary Examiner.

DAVID J. WILLIAMOWSKY, Examiner.

1. IN A FLUID POWER APPARATUS COMPRISING FIRST AND SECON ASSEMBLAGES OFMEMBERS, THE COMBINATION INCLUDING: A ROTATABLY MOUNTED APERTURED MEMBEROF PREDETERMINED LENGTH ASSOCIATED WITH THE SECOND ASSEMBLAGE WHEREIN INTHE APERTURE IS DEFINED, IN PART, BY AT LEAST ONE ARCUTATE SURFACECONCENTRIC WITH THE AXIS OF ROTATION OF THE APERTURED MEMBER, AND INPART, BY AT LEAST ONE ARCUATE SURFACE NONCONCENTRIC WITH THE AXIS OFROTATION OF THE APERTURED MEMBER, THE CONCENTRIC AND NONCONCENTRICSURFACES INTERCEPTING ONE ANOTHER LONGITUDINALLY OF THE APERTURE; AFIRST FLUID-CONVEYING DUCT SYSTEM IN THE SECOND ASSEMBLAGE COMMUNICATINGWITH A FIRST FLUID PORT LOCATED AT LEAST PARTIALLY IN ONE END OF ANONCONCENTRIC ARCUATE SURFACE ADJACENT TO A CONECNTRIC SURFACE; A SECONDFLUID-CONVEYING DUCT SYSTEM IN THE SECOND ASSEMBLAGE COMMUNICATING WITHA SECOND FLUID PORT LOCATED IN THE OPPOSITE END OF THE SAMENONCONCENTRIC SURFACE ADJACENT TO A CONCENTRIC SURFACE; A ROTOR OFGENERALLY CYLINDRICAL CONFIGURATION ASSOCIATED WITH THE FIRST ASSEMBLAGEHAVING A LENGTH ESSENTIALLY EQUAL TO THAT OF THE APERTURE OF THEAPERTURED MEMBER AND HAVING A RADIUS ESSENTIALLY EQUAL TO THAT OF THECONCENTRIC ARCUTATE SURFACE, THE ROTOR BEING LOCATED WITHIN THE APERTUREOF THE APERTURED MEMBER BEING ROTATABLE RELATIVE TO THE APERTURE MEMBERWITH ITS EXTERIOR SURFACE IN SUBSTANTIALLY FLUID-TIGHT RELATIONSHIP WITHTHE CONCENTRIC ARCUATE SURFACE, BUT SPACED FROM THE NONCONCENTRICARCUATE SURFACE BY A PREDETERMINED DISTANCE TO DEFINE A FLUID-FORWARDINGCHAMBER BETWEEN THE ROTOR AND THE NONCONCENTRIC ARCUATE SURFACE; A ROTORVANE CAMBER OF COMPLETE CYLIDNRICAL CONTOUR WITH A RADIUS LESS THAN THATOF THE ROTOR INSET INTO THE CYLINDRICAL SURFACE OF, AND AXIALLY PARALLELWITH, THE ROTOR WITH A SIDE OPENING THROUGH THE ROTOR SURFACE FACING THEWALL OF THE APERTURE IN THE APERTURED MEMBER; A ROTOR VANE HAVING ALENGTH ESSENTIALLY EQUAL TO THAT OF THE APERTURE OF THE APERTURED MEMBERLOCATED ROTATIVELY IN THE ROTOR VANE CHAMBER WITH ITS ROTATIONAL AXISCOINCIDENT WITH THE RADIAL CENTER OF THE ROTOR VANE CHAMBER AND FORMEDWITH THE ROTATIONAL VANE TIPS EACH EXTENDING PARALLEL WITH THEROTATIONAL AXIS OF THE VANE AND DISTANT THERREFROM BY A DISTANCEESSENTIALLY EQUAL TO THE RADIUS OF THE ROTOR VANE CHAMBER; MEANS TOCLOSE BOTH ENDS OF THE APERTURE OF THE APERTURED MEMBER TO PREVENTESSENTIALLY THE FLOW OF FLUID FROM THE ENDS OF THE APERTURE DURINGRELATIVE ROTATION OF THE FIRST AND SECOND ASSEMBLAGE WITH RESPECT TO ONEANOTHER; AND VANE ROTATING MEANS RESPONSIVE TO THE RELATIVE ROTATION OFTHE FIRST AND SECOND ASSEMBLAGES WITH RESPECT TO ONE ANOTHER TO CAUSEROTATION OF THE ROTOR VANE WITHIN THE ROTOR VANE CHAMBER TO CAUSE ONE OFITS TIPS TO WIPE THE SURFACE OF THE ROTOR VANE CHAMBER, THE PARTS BEINGDIMENSIONED TO CAUSE ANOTHER OF ITS TIPS TO WIPE SIMULTANEOUSLY ANONCONCENTRIC ARCUATE SURFACE.